Friction brake control system for centrifugal machines or the like



Dec. 26, 1950 J. HERTRICH 2,535,854

FRICTToN BRAKE coNTEoL SYSTEM FOR CENTETEUGAL MACHINES 0R TEE LIKE Filed Aug. 21, 1942 2 sheets-sheet 1 13E i 152 i INVENTOR. Jos 77H Hmm/CH A Trop/VHS J. HERTRICH FRICTION BRAKE CONTROL SYSTEM FOR CENTRIFUGAL MACHINES OR THE LIKE Dec. 26, v1950 2 sheets-sheet 2 Filed Aug. 21, 1942 w. m m m JOSEPH HE'QTR/CH MM zw@ A TTOIQNE YS Patented Dec. 26,; 1950 l PATENT OFFICE coN'rnoL" SYSTEM-f Fon fmrnnndan MACHINES on THELIKE 'f ioseplr Hertrichfnaniilton, Ohio, assigner to The Western StatesMachine Company, Hamilton,

'f "-Qhloi sf corporation of Utah Application Mgmt A21, 1942,"Serial No. 455,678

'"`2I`C' laim (Cl. 1884151) `This invention relatesfw-a'-fricton brake control system intendarleprimarily? for inl the braking or deceleration of `heavy rotating bodies. such ashigh speed-sugar centri-focus and 'other heavy duty machines virion-.operate infra cyclical manner with frequent accelerations-.andldecelen ations to and -from 1higl'i speeds of rotationV 'It also relates to the controlattention-clutches Vfor accelerating: heavy rotary bodies, arultofnew` :devices for` regulating -thepressure-supplied toa fluidpressure-fopelated-E clutch on the like.

Thel friction brakesfot-li-ighdrpeed-centrifugals, as heretofore `made and; Moedig-hare beenvappied by the force of 'springsforloflguid' creeis-under pressure so as to exert aia-approximately uniform :braking torque on thelrevolving mass from Lthe start to the end ofl each-braking period. ,l Simi larly, friction clutches commonly have beenmade to Work under a more or-lessilmifcrmcperating force. The braking-foperatlomfor example, -in volves the conversionof"` w creat dealo kinetic energy into heat AHthrough the friction of the brake. This heat is"notfdissipatedwsatisiactorily in .the v operation of somelheavwdutyhigh speed centrifugals, even thoughemcient `.wat'erjcooling systems and braking-elements of very-large surface area bevused. In-e'Xtremecases-the brake linings become `o ver-heatczlzA.and weer` out after only a few weeks of servicepnndthefbrake drums Vmay even become checkedfl or-cracked from ex cessive heat, suchthattheymustbefreplaced to avoid danger or breaking. Asbrakeflnings become over-heated the brakingeperiodi-foff each .centrifugal cycle-.is extended@ atL .aloss;l ofmachine capacity, and-.the .repiaeementfofcworn out.

ruptions to service. f

It istherefore, the object-or my-presentinven vtion to provide `aineer-andi'xxiproved control-.sys-

linings entails objectionable expenses and inter- .like by whichto alleviatefproblemso! the-kind just described. Anotherl'ohieetfis-tofecctthe heat generation duringfthc` breaking or clutching l period than heretofore,--f'so-that the" heatgenerated may be dissipated'morc" readiiy- 'byiliitable brake coolingmeans. kvUrli. intenti-lo: 2,(l9l '3il of Eugene Roberts, reissued underNozReZiGil,

discloses an ellcient-l cooling-1: iiieaxlsA `suitable for centrifugal brakes. f 'Still-another object 'of the invention `is toprovide-a` systemd'or retardingl or accelerating the rotation '0f high speed-"centrifu- :2 gal machines, or of other heavy bodies or masses, which reduces the danger of over-heating Vthe friction elements without prolonging the period required forthem to eiectuate the desired speed change.

A further object of the invention is to provide novel ,means or devices for increasing at a regulated rate, from a relatively low initial value, the fluid pressure supplied to an object from a source of relatively high iluidpressure.

VI have observed operations of heavy-duty high `speed centrifugal machines equipped with friction brakes in which the heat generation during braking was so intense that the brake linings smoked and the friction surfaces of the brake drum be-` came almost red hot, notwithstanding the presence vof ample cooling Water against the inside wallof the drum. From such observations I coneluded that the rate of heat generation during braking was greater than the rate of heat transmission through the Wall of the brake drum, such that over-heating necessarily occurred and could be avoided `with known equipment only by re- ,ducing the braking force and extending the brak- `maybe comparatively 10W. Following this I conceived Vthat the problem of excessive heat peaks mightbe-overcome if the initial braking force wereestablished at a. low enough value to keep 'the heat generation atithe fastest speeds Within thel-heat-disspating capacity of the brake system, and if the braking force were increased substantially in the course of the braking operation, `asthe speed of the massbecome substantially re duced. Such a practice would cause more uniform heat generation during the braking period and reduce heatrpeaks and over-heating problems, but it-need not prolongthe braking operation becau-sea faster rate of deceleration could Vbe obtained -in the lower range of speeds, sufmethods and apparatus for the control of friction brakes, friction clutches, or thev like, as set forth in the appended claims and as described more particularly hereinafter with. reference to the specific embodiments illustrated in the accompanying drawings, wherein:

Figure 1 shows a heavy-duty centrifugal machine equipped with a friction brake and a brake control system according to a preferred embodi ment of the invention;

Figure 2 is a horizontal section showing the braking members and the air cylinders which apply the brake;

Figure 3 is an enlarged sectional View showing details of the principal control elements of Figure l;

Figures 4, 5 and 6, respectively, are diagrammatic illustrations of modied brake control systems embodying the invention.

The systems provided by this invention, broadly speaking, utilize a new method for controlling heat generation during the changing of speed of a heavy revolving body by friction means such as a friction brake or clutch, in which the brake, for example, is applied with a limited force during the fastest rotation of the body and in which the braking force is substantially increased as the speed of the body is reduced. The initial braking 4 pressure line is vented upon the closing of valve 22.

Figure 5 shows an embodiment similar to that of Figure 4 in which, however, the brake is adapted to be actuated by oil or other liquid under pressure. Here the conduit leading from the bleeder hole 26 to cylinder J8 is connected with a sealed air chamber 3 so that liquid bleeding through the hole 26 builds up full pressure in the force preferably is predetermined in such relation Y to the speed and mass of the body as to keep the heatgeneration within the heat-dissipating capacity of the brake system, and as the deceleration proceeds the braking force preferably is in creased in timed relation to the decrease in the speed oi the body, such that the desired braking eiiciency and short braking period are obtained without increasing the rate of heat generation. In the case of a friction clutch the relation of the machine speed to the force or pressure of the friction means is simply reversed.

According to the preferred embodiment illustrated in Figures l to 3, the braking force is increased gradually and at an approximately constant rate from a predetermined minimum at the force may be obtained in various ways, e. g., as il- I lustrated in. Figures 4 and 5 of the drawing; or a gradual increase from any desired initial braking force may be obtained as illustrated in Figure 6.

Referring first to the embodiment of Figure 4, a brake drum i!! carried by a shaft l2 is shown diagrammatically as working with a brake band I4 which is connected to a plunger I8 of an air cylinder I8 so as to be applied by the force of compressed air admitted into the air cylinder. The compressed air is supplied through a' pres.- sure line 29 which has a cut-off valve 22, such as a conventional three-way solenoid valve, to control the setting and unsetting ofthe brake. Air pressure is transmitted from valve 22 to cylinder |18 through a by-pass 24 having a 'small bleeder hole 26 which throttles the air Ilow and so delays the building up of full pressure in the cylinder i8. A pressure release line 28 has a one-way check valve 29 therein which permits instantaneous release of pressure from the air cylinder when the vbraking force of any desired value, by transmitting uid pressure from the cut-oi valve 22 to the brake cylinder I8 vthrough a suitable pressureregulating valvea and utilizing the bleeder hole actiontoI increase the pressure established by the pressure regulating valve. One arrangement of that type is shown diagrammatically in Figure 6, wherein the pressure' line"2fisf connected with the cyunder 1s, eirect-iytnrougn pressure-regulating valve 32 and'indirec'tly'thrugh a by-pass 34 having 'parallel'branches; 36 and 38, one with the bleeder 2th'erein andthe other with the check valve 129. Isi'rigQ` for example, a compressedjair supply 'at a pressure of 80 pounds per square inch, the valve 32" may be set to give an initial braking f iiespondin'g to a pressure of 40 pourilsfpersa` inchfinfcylinder la, when thel cut-off valve-'22 y ope'e'dfa-fter which press'urebl'ds graduali throug-lithe bleeder hole 26 until 'a *maximumpressure*"-'approximating 80 pounds per square inch has been attained, say after-'2O seconds orso of braking. Another larrangnner'-it of the type last referred to is represented :bythe preferred-embodiment of Figures 1 to 3,;wh'i'c'h`h'as'certain fea/tures andadvantages not common to th'eother illustrated embodiments. In pa'rticula'rr'the rate'of increase of the braking'fo'rce" isheld constant at any selected value; and the u-llbra-ki-ng force is obtained even Where the:I air cylinder leaks pressure, which may not betrue of' ot er m's'vvhere the'full force of 'the brak'eisrea onlyfby the'slow bleeding of fluidthrough thfeb r" hole:- 'Figures l to 3 show the' invention as"applied inthe preferred mannerffto an 'airbperated brake onlarhigh speed sugar centrifugal-,fand 'they also show ableeder means 'and af -heckl "v"e, or; pressure-release means; asbeingcombned'yinfa. common unit for simplicity andl 'economy 'of construction.-

Referring t`o` Figure l,E the centrifugal machine comprlses'a baas-k Dil suspended by aspindle m2 from aig-yiatery eaesepportedbelowframework F. A 'motor 1Mf`^drivesl the-spindle and basket through intermediate connections not shw'n brake drinn* |64 rotates! with the spindle and basket assembly 'and cooperates with brake` ba-"nds"4 T05 and-'|568 (Figure 2)',-Whi`ch have suitablef` irictn -liiiin'gs L. One end of each brake band isanhored on a bracket -I lil, and the other 'end' 'is 'connectedby a bracket andpin I|2 with the 'piston-I Hi `ofan" airv cy1inde1'-"ll8. A spring H4 'in 'ea'chlcyl` "der-` tends totmove the brake to the. foif 'o y.released position; Compressed 'airffren fa suitable "source (not shown) is ad'aptedtd beadmiftted 'intol the cylinders H8 through'a supp1y-1mefi20sr vfA-cut-orf valve |22, 'uch asasiiitable threelwaysolenoid valve, controls'the airfs'iippl'y.

`LAs shown in Figures l'and 3, the control system further-includesf a'variable pressure-regulating valve 132 across the' air line |2 between the cutofE valvelit22'and-'the 'air' cylinders H8.

with said diaphragm, tubing connecting said chamber with said conduit between said pressure-regulating valve and said cylinder, bleeder means in said tubing to transmit pressure established by said pressure-regulating valve gradually into said chamber, and a check valve in said tubing to release pressure from said chamber upon the venting of said conduit.

4. A heavy rotary machine including a friction means applicable to a rotary part of the machine to change its speed, an air cylinder to apply the friction means, and means for supplying compressed air to said cylinder, wherein said supplying means comprises a pressure-regulating valve operative to establish a predetermined minimum pressure in said cylinder when said air supplying means is rendered active, together with an air chamber operative upon an increase of pressure therein to increase the pressure established by said valve, and means including an air conduit having a bleeder hole therein for gradually transmitting pressure acting upon said cylinder into said chamber.

5. A heavy rotary machine including friction means applicable to a rotary part of the machine to change its speed, an air cylinder to apply the friction means and means for supplying compressed air to said cylinder, wherein said supplying means comprises a pressure-regulating valve operative to establish a predetermined initial pressure in said cylinder when said'air supplying means is rendered active, together with an air chamber operative upon yan increase of pressure therein to increase the pressure established by said valve, and means including an air conduit having a restricted passage therein for gradually bleeding air pressure established by said valve into said chamber, said :conduit also including a check valve to release -air pressure from said chamber when the compressed -air supply is cut o.

6. In a heavy rotary machine comprising fluidpressure-operated friction means applicable to a rotary part of the machine to change its speed, means for controlling the operation of said friction means comprising a pressure fluid conduit having a pressure-regulating valve therein and a portion leading from the outlet side of said Valve to said friction means, said valve having yieldable means urging the same open with a predetermined force and means responsive to the iluid pressure in said outlet portion to urge the valve closed in 'counteraction to said yieldable means, secondary means for applying fluid pressure to said valve so as to urge the same open with force additive to said predetermined force, and means for gradually building up fluid pressure in said secondary means over a substantial time interval, so' that the pressure in said outlet portion may be increased correspondingly during said interval.

7. In a heavy rotary machine comprising fluidpressure-operated friction means applicable to a rotary part of the machine to change its speed, means for controlling the operation of said friction means comprising a pressure fluid conduit having a pressure-regulating valve therein and a portion leading from the outlet side of said valve to said friction means, said valve having yieldable means urging the same open with a predetermined force and means responsive to the uid pressure in said outlet portion to urge the valve closed in counteraction to said yieldable means, secondary means for applying fiuid pressure to said valve so as to urge the same open with force additive to said predetermined force,

and a branch conduit containing a restricted passage to bleed pressure iiuid slowly from said outlet portion to said secondary means, so that thepressure in the latter increases gradually at a substantially constant rate and the pressure in said outlet portion increases correspondingly from an initial value established by said predetermined force to a higher value supplied in said line.-

8. Apparatus as described in claim 7, said branch conduit having a return passage arranged to bypass said restricted passage and a valve across said return passage operative to release the uid pressure in said secondary means when the same exceeds the iluid pressure in said outlet portion.

9. In a heavy rotary machine comprising fluidpressure-operated friction means applicable to a part of the machine to change its speed of rotation, means for controlling the operation of said friction means comprising a pressure fluid conduit having a pressure-regulating valve therein and a portion leading from the outlet side of said valve to said friction means, said valve having a spring to urge the same open witha predetermined force and a diaphragm responsive on one side to fluid pressure in said outlet portion to urge the valve closed, a fluid pressure chamber communicating with other side of said diaphragm, and means for gradually building up fluid pressure in'v said chamber.

10. Apparatus asdescribed in claim 9, said means for gradually building up uid pressure in said chamber comprising a branch conduit connecting said outlet portion with said chamber and containing a restricted passage operative to bleed uid slowly into the chamber when the pressure therein is less than the pressure in said outlet portion.

11. Apparatus as described in claim 10, said branch conduit having a return passage arranged to bypass said restricted passage and a check valve across said return passage operative to release the fluid pressure in said chamber when the same exceeds the fluid pressure in said outlet portion.

l2. Apparatus as described in claim 11 wherein said restricted passage is located in the movable element of said check valve.

13. In a heavy rotary machine comprising fluid-Pressure-operated friction means applicable to a rotary part of the machine to change its speed of rotation, means for controlling the operation of said friction means comprising a pressure fluid conduit having a pressure-regulating valve therein and a portion leading from the outlet side of said valve to said friction means, said valve having. a spring to urge the same open with a predetermined force and a diaphragm responsive on one side to fluid pressure in said outlet portion to urge the valve closed, a fluid pressure chamber communicating with the other side of said diaphragm, means for gradually building up iiuid pressure in said chamber to urge the valve open with force additive to the force ofl said spring, and means for adjusting the setting of said spring to change the force thereof.

14. Apparatus as described in claim 13, wherein said spring is a compression spring bearing at one fend against said other'side of the diaphragm and said adjusting means includes a member screw threaded in a part of said chamber, bearing against the other end of said spring, forming a passage `for pressure uid, and accessible through said chamber for adjustment to change the compression of the spring.

15. A iiuid pressure regulating device comprising a pressure fluid conduit having a valve therein and inlet and outlet portions on the respective sides of said valve, yieldable means urging the valve open with a predetermined force, means responsive to the iiuid pressure in said outlet portion to urge the valve closed in counteraction to said yieldable means, secondary means for applying iiuid pressure to said Valve so as to urge the same open with force additive to said predetermined force, and means for gradually building up fluid pressure in said secondary means over a substantial time interval so that the pressure in said outlet portion may be increased correspondingly during said interval.

16. A device as described in claim 15 wherein the means for building up fluid pressure comprise a conduit containing a restrictive passage arranged to bleed fluid slowly from said outlet portion to said secondary means, so that the pressure increase may occur at a substantially constant rate dependent upon the size of said passage.

17. A fluid pressure regulating device comprising a pressure fluid conduit having a valve therein and inlet and outlet portions on the respective sides of said valve, said valve having a spring to urge same open with a predetermined force and a diaphragm responsive on one side to fluid pressure in said outlet portion to urge the valve closed, a. uid pressure chamber communicating with the other side of said diaphragm, and a branch conduit connecting said chamber with said outlet portion and containing a restricted passage operative to bleed fluid slowly into the chamber from said outlet portion when the pressure in the latter exceeds the pressure in the chamber.

18. A device as described in claim 17 wherein said branch conduit has a return passage arranged to bypass said restricted passage and a check valve across said return passage operative to release the pressure in said chamber when the same exceeds the pressure in said outlet portion.

19. A device as described in claim 18, said restricted passage being located in the movable element of said check valve.

20. In a braking system for a heavy centrifugal machine comprisinga shaft connected for rotation with the basket of the machine, a brake drum on said shaft and a friction device applicable to said drum for decelerating the machine from a high speed of rotation at frequent intervals, uid pressure responsive means connected with said device for applying the same, a fluid pressure conduit connected with said applying means for conducting fluid pressure thereto from a source of a predetermined maximum fluid pressure, a pressure cutoff valve in said conduit, a pressure-regulating device in said conduit between said cutoff valve and said applying means, said regulating device being operative upon the opening of said Valve to transmit to Said applying means a limbut sufficient to decelerate the machine, and pressure bleeding means connected with said conduit and rendered operative upon the opening of said valve to increase the pressure acting upon said applying means gradually from said limited pressure to approximately said maximum pressure during a maj er interval of the deceleration period, so that the rate of brake heat generation in decelerating the machine from said high speed is nearly the same at the end of said interval as it is at the beginning thereof.

21. In a braking system for a heavy centrifugal machine comprising a shaft connected for rotation with the basket of the machine, a brake drum on said shaft and a friction device applicable to said drum for decelerating the machine from a high speed of rotation at frequent intervals, uid pressure responsive means connected with said device for applying the same, a uid pressure conduit connected with said applying means for conducting fluid pressure thereto from a source of a predetermined maximum iiuid pressure, a pressure cutoff valve in said conduit, a pressure-regulating device in said conduit between said cutoff valve and said applying means, said regulating device being operative upon the opening of said valve to transmit to said applying means a limited pressure much below said maximum pressure but suiicient to decelerate the machine, said conduit having a branch line interconnecting portions of it on opposite sides of said regulating device to bypass the latter and a pressure bleeding device in said branch line operative upon the opening of said valve to increase the pressure acting upon said applying means gradually from said limited pressure to approximately said maximum pressure during a major interval of the deceleration period, so that the rate of brake heat generation in decelerating Vthe machine from said high speed is nearly the same at the end of said interval as it is at the beginning thereof.

JOSEPH HERTRICH.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 468,917 Moore Feb. 16, 1892 678,352 See July 9, 1901 865,732 Vandernell et al. Sept. 10, 1907 960,055 Sundh May 31, 1910 1,088,744 Thurber Mar. 3, 1914 1,390,597 Westinghouse Sept. 13, 1921 1,733,898 Moore Oct. 29, 1929 2,090,460 Schaum Aug. 17, 1937 2,096,341 Roberts Oct. 19, 1937 2,453,854 Olcott Nov. 16, 1948 

